Centrifugal cutter with automatic balance



July'7, 1970 v R. A. PETERSON .ETAL 3,519,047

' CENTRIFUGAL CUTTER WITH AUTOMATIC BALANCE Filed Feb. 13, 1968 v 2Sheets-Sheet 1 FIG 6.

INVENTORS ROGER 1 A. PETERSON JOHN PAUL ELSON CHARLES R. SMITH BY LLOYDD. SLAGELL ATTY'S.

July 7,1970 R, T R ETAL 3,519,047

CENTRIFUGAL CUTTER WITH AUTOMATIC BALANCE Filed Feb. 13, 1968 r 2Sheets-Sheet 2 I44 7 I42 I84 48 I00 INVENTORS, ROGER A. PETERSON JOHNPAUL ELSON CHARLES R. SMITH LLOYD D. SLAGELL United States Patent3,519,047 CENTRIFUGAL CUTTER WITH AUTOMATIC BALANCE Roger A. Petersonand John P. Elson, Peoria, Charles R.

Smith, Pekin, and Lloyd D. Slagell, Peoria, 111., assignors to CreveCoeur Mfg. C0., East Peoria, Ill., a corporation of Illinois Filed Feb.13, 1968, Ser. No. 705,125 Int. Cl. A23n 1/02 U.S. Cl. 14676 ClaimsABSTRACT OF THE DISCLOSURE The disclosure describes a centrifugalcutting device having means to continuously orient the rotating masscenters of certain corotating parts in relation to the stationaryresiliently mounted mass and thereby provide vibration-free uniformcutting action. In one embodiment a flat circular cutter blade isresiliently mounted on a shaft for both axial and radial movement from apivotally mounted plate within the housing of a driven flywheel on thereference axis. The pivotal means comprises a ball and socket joint inthe drive shaft in combination with a radially displaced resilient drivepin in a centrifugal type juicing machine wherein variations in thecutting rate affects the amount of unbalanced macerated mass distributedto a centrifugating basket and the combination controls both static anddynamic balance of the rotating parts to continuously orient the masscenters, redistribute the centrifugating cuttings to restore equilibriumand maintain uniform cutting action. Other embodiments are disclosed.

CROSS REFERENCE TO A RELATED PATENT The instant invention represents animprovement over the invention described andclaimed in Smith et a1. Pat.No. 3,407,858. The entire disclosure of said patent is herebyincorporated by reference into the instant application.

BACKGROUND OF THE INVENTION In accordance with said Pat. No. 3,407,858,the dynamic and static balance of high speed rotating parts ismaintained by providing a cutter drive and mounting which allows therotating parts to cant out of the normal plane of rotation at a pointdiametrically opposite a point of imbalance and thereby cut deeper intothe stationary workpiece, to create and deposit increased cuttings in anamount proportional to the imbalance and automatically deposit thisproportional mass at said diametrically opposite points. The means toallow the rotating parts to cant described in said co-pendingapplication included a resilient sleeve to provide limited radial andcircumferential movement between the driven means and the cutter meanswith means to resiliently hold the cutter axially against the drivenmeans.

SUMMARY OF THE INVENTION In accordance with this invent-ion an improvedvibration dampening effect along with simultaneous re-orientation of thereference and whirl axes is obtained by supporting the driven means on apivot pin at the reference axis between means to provide limited radialand circumferential movement between the driven means and the workingmeans or cutter. In a particular embodiment of this invention a driveaxle is provided carrying a primary flywheel. The flywheel has a housinginto which is spacially fitted a movable, balanced flywheel plate. A

primary drive pin connects the primary flywheel with the flywheel plateand a resilient means is interposed between the primary drive pin andthe flywheel plate. A pivot pin or ball and socket joint carries theflywheel plate 'ice central of the drive axle with slight axialdisplacement and slight radial displacement provided by the housing. Thework means or cutter is mounted therefrom on a second drive pin withboth axial and radial displacement by the cap means of said c0-pendingapplication.

More particularly, this invention provides a high speed machine adaptedto macerate juice-containing fibrous materials having a verticalrotatable shaft, a centrifugal flywheel hub mounted on and adapted torotate with the shaft, a perforated cylindrical walled basket carried bythe flywheel hub and a fixed tube to introduce the fibrous materials,wherein a cutter disc is mounted on the base plate of the basket, theflywheel hub has a housing with balance flywheel plate in the housingand pivot or ball and socket means mounting the cutter disc, basket andbalance flywheel plate central of the flywheel hub whereby any imbalanceof the basket or cutter is translated into increased cutting action atthe fixed tube to offset the imbalance by depositing additional cuttingsdiametrically opposite the imbalance.

Accordingly, the objects of this invention are to provide simple,practical and effective drive mounts for the working elements of highspeed rotary machines to reduce vibration due to working imbalance insuch machines, to provide a floating centrifugal hub mounted on a pivotpin within a hub housing adapted to provide limited opposite radial,axial and combination radial-axial movement of the floating hub, and toprovide means for mounting centrifugal working means from the floatinghub whereby the machine is self-balancing both statically anddynamically. These and other objects will become apparent or bedescribed as the specification proceeds.

DESCRIPTION OF THE DRAWINGS Reference is made to the drawingsillustrating an embodiment of this invention wherein:

FIG. 1 is a partial side elevation view of the vegetable juicing machineincorporating the improvements of this invention;

FIG. 2 is a partial sectional view, enlarged to show the drive, cutterand hub assembly of this invention;

FIG. 3 is a partially exploded view, in cross-section of the parts shownin FIG. 2;

FIG. 4 is a diagrammatic view illustrating in a plane motion model, thedynamics of the centrifugal system during a condition of imbalance;

FIG. 5 is a diagrammatic View illustrating in a plane motion model thedynamics of the centrifugal system as the condition of imbalance iscorrected; and

FIG. 6 is a diagrammatic view of these conditions translated to themachine to show that the imbalance is opposite the machine axis ofrotation and that the wheel axis of rotation of the basket is parallelto the reference axrs.

THE PREFERRED EMBODIMENT Referring to FIG. 1, there is shown avegetable-shredder and centrifugal juice extracting machineincorporating the drive and mounting of this invention by way ofillustration, wherein a base housing member 10 supports and contains adrive motor (not shown), including the necessary electrical conduit andswitch for its operation. The lower portion of the housing 10 isconventionally equipped with rubber foot elements 11 or equivalentdevices to frictionally support the device on a horizontal surface withsome resilient movement. A pair of oppositely disposed side supports 12extend upwardly from the housing 10, and have oppositely facing recesses14, hearing thumb screws 16 thereabove, designed to secure the radialears 18 of the removable cover member 20. In its secured position thecover member 20 fits over the top of and closes the vessel 22, formingan enclosure to catch juices produced by the device.

The vessel 22 is removable and has a circumferential trough bottom 24into which the juices collect for removal through a downwardly dependingspout (not shown) communicating with the trough. The inner wall of thetrough bottom 24 is formed into an up-turned circumferential flange 26having a central opening 28 to receive a balanced flywheel hub member30. The flange 26 is slightly off-set, as shown, to provide a retainingsurface which engages and rests upon the upper edge of the housing 10.The flywheel hub 30 has a plurality of radial vanes 32 on its under sideand is mounted for rotation at high speeds by the drive shaft 34,connected in turn to a drive motor (not shown) mounted within housing10. The upper edge of housing 10, as well as the bottom of the deviceare provided with passageways (not shown) for the forced circulation ofcooling air by the vanes 32 around the drive motor.

The flywheel hub 30 and shaft 34 carry a conventional basket 38 having abottom wall 40 and perforated cylindrical side wall 42 with an openinwardly depending top rim 44.

A macerator disc 46, having a plurality of substantially radiallyarranged cutting teeth 48 on its top surface, is mounted axially of theshaft 34 contiguous to the bottom wall 40 of the basket. The cover has avegetable feeding guide tube 50 formed integral therewith, which is openat the top and extends downwardly into the basket 38. The lower open endof the guide tube 50 is closely spaced from the macerating disc 46, asindicated at 52, at an off-center point in registry with the pattern ofthe cutting teeth 48 on the maceraing disc. This assembly of maceratingdisc 46, basket 38 is held together by means of the cap member of leadnut 54 which is attached to a ball and socket pivot pin and floatingflywheel hub to the shaft 34 in a manner to be described. The rotationof the shaft 34 causes the hub 30, the basket 38, the macerator disc 46and the cap member 54 to rotate, which parts constitute the principalelements subjected to imbalance during use of the machine. Duringoperation, the material to be macerated is gradually introduced into theguide tube 50 into contact with the cutting teeth at the space 52. Theresulting fibers and juices are flung outwardly and caught by the wall42. The juices passes through the perforations and the fibers areretained on the inside circumferential surface of the basket. Ifdesired, an elongated filter paper or fibrous mat can be placedcircumferentially around and against the inside of the wall 42 to catchthe finer vegetable or other types of pulp produced by the juicer.

It is seen that the device as thus far described is readily assembledand disassembled. Removal of the cover 20 is accomplished merely byloosening the thumb screws 16, turning the cover 20 clockwisesufliciently to clear the ears 18 therefrom from the recesses 14 andraising the cover from the device. By unscrewing the cap 54 themacerator disc and the basket 38 can be lifted from the assembly. Thisallows ready removal of the vessel 22 for cleaning, etc. All parts aremade of corrosion resistant metal and are fabricated with smoothsurfaces and rounded corners where possible to exclude undesiredaccumulations of food particles and juice residues.

It is apparent that the introduction of vegetables, fruits and the likethrough the feed guide tube 50 into contact with the macerating disc 46at the space 52 produces a continuously increasing mass of fibers on theinner wall of the basket, which mass is directly proportional to thecutting rate at any moment of time. Normally, a wooden pestle (notshown) is provided for insertion into the tube 50 to force thevegetables downward upon the rotating disc 46. The pestle would have ashoulder larger than the opening in the tube 50 to prevent its contactat the lower end with the teeth 48. The juices pass through theperforations of the wall 42 and are collected in the bottom 24. Somefibers are retained or caught by the teeth 48 of the rotating disc 46.The accumulations of fibers on the rotating parts are not uniformbecause of variations in cutting rates and as the juicing operationproceeds there is developed periodic imbalance in these rotating parts.At speeds of 2000 rpm. or faster any imbalance of these principleelements disturbs the rotational equilibrium of the device and severevibrations of the device can develop unless means are provided tocounteract the disturbing influences. The existence of an imbalance alsohas an influence on the cutting rate and the harmonic motions developedin the parts can further accentuate the disturbance of the equilibriumof the rotating system. Part of this vibration is offset by the actionof the cap member 54, as described in said copending application.

In accordance with this invention, means are provided to cooperate withsaid cap member 54 for automatically and continuously maintaining therotational and dynamic equilibrium of the parts so that at no timeduring operation of the device does the vibration become excessive andany vibration caused by uneven distribution of fibers in the basket iscounteracted. It has been found that more complete and continuouselimination of vibration can be attained by supporting the basket andcutter on a pivotally mounted plate driven by the flywheel.

The details of the structures to accomplish these results are shown inFIGS. 2 and 3 wherein the drive shaft 34 is shown to have a weightbearing shoulder 56 adjacent the bottom of the centrifugal flywheel hub30 with the threaded spindle 58 extending into and engaging the threadedbore 60 located central of the hub. The drive shaft 34 is directlyconnected to a source of rotational power such as an electric motor.

The primary flywheel hub 30 has a threaded bore 60 within the centerblock or nave 62 and is formed with an inner annular recess 64 and aperipheral flange 66, with a pair radial bores 68 extending from therecess through the outer body of the hub to the outer wall 70 definedabove the flange 66. A flat top surface 72 is provided on the hub 30extending from the central enlarged recess 74 in the nave 62 whichcommunicates with the threaded bore 60.

A separable retainer ring with an annular base 82 encompasses the outerwall 70 of the hub 30. A pair of radial bore holes 84 extend through thebase 82. The pp r end of the ring 80 has a circumferential shoulder 86which rests upon the outer periphery of the surface 72 and is formedwith an annular flange 88 extending radially inward from the top surface90. The ring 80 is adapted to fit over and encompass the outer surface70 of the hub 30 with the bores 84 registering radially with the bores63 so that each can receive a shear pin 92, only one of which isillustrated. If desired only one pair of matching bores 68 and 84 can beused in the flywheel assembly. The bottom of the base 82 of the ring 80is spaced axially from the flange '66 as indicated at 94.

The hub 30 has a drive pin 96 press-fitted into a suitable bore in thetop surface 72 and axially spaced between the oppositely facing recesses74 and 64. The pin 96 extends above the surface 72 and has a resilientdrive washer 98 encompassing this extended end.

A balance disc or upper flywheel 100 is contained within the ring 80 bymeans of the opposed positions of the flange 88 and the lower outwardlyextending flange 102 of the disc. The disc 100 has a central threadedbore to receive the pivot pin 104, having at its lower end a ball joint106 and threaded shank 108 at the upper end. The pivot pin 104 extendsbelow the bottom surface 110 of the disc 100 into the central recess 74and is axially aligned with the bore 60. The upper end of the threadedshank 58 of the shaft 34 has a recess or socket end 112 adapted toreceive and mate with the ball joint 106 with a non-frictional pivotalaction between these parts. Pin 104 and the shank 58 are adjustable toeach other so that the space 114 between the surfaces 72 and 110 can bevaried as desired Within the limits allowed by the spacing of the flange88 over the flange 102.

The disc 100 has a recess 116 in its bottom surface 110 to engage thedrive pin 96 and the resilient washer 98. The recess 116 is slightlylarger than the outer circumference of the washer 98 so as to leave aspace 120 therebetween. Also the recess 116 has a generally conical topwall 122 so that the top peripheral corner of the washer 98 engages samein a circumferential point contact. This edge contact arrangementimparts a greater degree of resiliency to drive action of the drive pin96 than side wall contact and makes assembly and disassembly easy. Thedisc 100 is further dimensioned so that it is spaced peripherally fromthe retaining ring 80 as indicated by the annular spaces 124 and 126which extend about the circumferences of these parts. The disc 100 alsohas a recess 128 in the top which defines a circumferentialweight-bearing surface 130 around the outer edge of the disc 100. Withthe ring 80 in place over the hub 30, the disc 100 is held between thepivot 106-112 and the opposing contact between the flange 88 and theflange 102 in a resilient movable manner as will be described.

A second drive pin 132 is fixed within the body of the disc 100 andextends upwardly through the bore hole 134 of the bottom 40 of thebasket 38. Likewise, central of the bottom, the bore hole 136 of thebasket receives the top end of the pivot pin 104. The macerator disc 46has a central bore 138 and a smaller bore 140, to receive the pivot pin104 and second drive pin 132, respectively. Both the bores 134 and 140are slightly larger than the drive pin 132, so that the spaces 142 and144, therebetween, produce a slight play between these parts.

The bottom surface 146 of the basket 38 rests upon the circumferentialsurface 130 of the disc 100. The shank 108 of the pivot pin 104 extendsthrough the assembled parts as an extension of the axis of the shaft 34where it is engaged by the cap member 54.

The cap member 54 has the central threaded bore 152, engaging the shank108 and a smaller bore 154 extending from the shoulder 156 to thechambered top. A transverse bore 158 extends radially through the capand intersects with the bore 154. The transverse bore 158 is for thepurpose of inserting a pin wrench to tighten or loosen the cap from itslocked position on the pivot pin 104.

A plunger sleeve 160 encompasses and is slidably mounted on the body ofthe cap 54 and is held thereto in a downwardly biased position by meansof the compression spring 162, held between the shoulder 164 of theannulus 166 and the internal radial flange 168 of the sleeve. A C-ringor spring washer 180 engaging a circumferential groove at the base ofthe plug member provides the means for retaining the sleeve 160 inplace. The spring 162 allows the sleeve 160 to be moved axially of theassembly. When tightened in place on the pivot pin 104, the bottomperipheral surface 182 of the sleeve impinges against the top surface184 of the cutter disc 46 and the base of the plug is spaced therefromas at 186. This gives a slight axial and canting resilience to thecutter on the pivot pin 104 in cooperation with the spaces 142 and 144around the drive pin 132. The unthreaded portion 188 of the shank 108 islong enough to engage the bores 136 and 138 in the sliding clearance fitsupra.

The balancing members so far described have the following features andmeet the following requirements: The basket 38 and the cutter 46 arefree to tilt quite freely through a very small angle defined and limitedby the spacing of the parts. The basket and cutter are also rigidlyrestrained from tilting any further than this small limited angle. Theseparts are free from any tendency to vibrate or create vibrational noise.The tendency for liquids to leak into these parts is mitigated orprevented. The structure is simple so that the parts are readilyfabricated, assembled, adjusted and maintained.

The combination of the pivot pin 104, the resilient drive pin 96 and thespacing of parts comprise a spring pivot which keeps the upper flywheeldisc 100 centered with respect to the axis of rotation of the hub orlower flywheel 30. The spring pivot oifers very little resistance to thetilting action of the disc 100 and holds this part tightly against theouter restraining ring and thus reduces the possibilities of vibrationand vibrational noise from the disc during high speed operations. Theflywheel hub 30 and the ring 80 operate as a unit and the pivot pin 104imparts a spring pivot action strong enough to keep the disc 100 tightlyagainst the flange 88 and allow movement provided by the spaces 124 and126. At the same time the disc 100 is prevented from movement in avertical or axial direction.

The ring 80 acts as a collar for the upper flywheel disc 100 holding theunwanted deflections to a minimum and preventing harmonic motions of theresiliently suspended parts. By restraining the flywheel dlisc 100 atits outermost edges instead of at its center and at its outer edges, theforces produced between the upper flywheel and its mating parts are heldto a minimum and deflections are reduced. The collar effect of the ring80 also provides definite and limited restraint of the upper flywheel100 about any horizontal axis within the spaces 124 and 126 into whichthe forces may tend to cause it to tilt. The resilient drive pin 96-98combination reduces vibrational noise due to torsional vibration betweenthe upper and lower flywheels. Since the flanges 102 and 88 are insubstantially constant axial pressure against each other, thepossibility of liquids leaking into the spaces 114 and 126, and therecess 74 is minimal.

Referring to FIGS. 4, 5 and 6, the dynamics of the system will now beexplained. M represents the effective mass of the entire machine body 10while In represents the concentrated mass of the rotary basket 40 andthe cuttter blade 46. The spring forces K represent the effectiveelasticity of the vibration dampening forces or isolaters acting in theplane of vibration of the system.

Under normal conditions the center of mass m will be coincident with thecenter line CL of the entire system. FIG. 4 illustrates the conditionwherein the center of the mass m has been moved a radial distance e fromthe center of the machine axis of rotation. This condition results froman imbalance in the basket or cutter or both due to the unevendistribution of fibrous residue during the high speed juicing process.It can be shown that the horizontal motion of the mass M in thedirection of the arrow x is given approximately by the equation:

where w is the constant speed of the motor and W1 represents the angularvelocity of the mass m in the quadrant shown. A similar equation existsfor horizontal motion in the y axis direction and for each quadrant ofrotation about the center line. By defining r as the ration of the motorspeed to the natural free vibration of the system in the horizontalplane, the motion of the mass, M in the x direction in quadrant shown iswherein A is a constant having a value of less than 1.0, since m M.

Equation 3 illustrates that the mass center mi of the rotating basketand blade is displaced opposite the ma chine axis of rotation C by thedistance and direction x shown in FIG. 5. The basket and bladecombination mass m rotates around the displaced center C and the mass Mwhirls or oscillates around the whirl axis C.

In FIG. 6 this relationship has been translated into a diagrammaticrepresentation of the parts of the instant apparatus where C is thewhirl axis of the mass M, C

is the original center line of rotation, the basket and cutter aredesignated by their reference members, and a is the tilt angle on thepivot 196. The stationary tube 50 is shown in two positions of rotationto illustrate that the cutter disc is tilted closer to the tube 50 whenthe mass m is opposite thereto and away from the tube 50 when the mass mis in the same quadrant as the tube 50. As the mass m of debris passesin the position shown, the pivot 106 allows the rotational plane threofto remain independetn of the whirl c of the mass M. This brings thecutter 40 into closer contact to the tube 50 by the amount of the tiltangle a. And as the mass m passes the fixed tube 50' the cutter 40 isinclined away from the tube 50 by an amount equal to the tilt angle a.In other words the plane of rotation of the cutting blade and the mass mis independent of the whirl axis of the mass M by an amount equal to thetilt angle a due to the pivot axis 106.

It is apparent from the foregoing that the pivot 106 allows the rotatingelements to shift slightly radially and also tilt upon the axis 34 underthe yielding action of the drive pin 96, the resilient holding action ofthe cap member 54 and the tilting support of the flywheel disc 100within the spaces 124 and 126. The spaced relation of the drive pin 132does not interfere with this action.

To provide at least part of this resiliency the washer 98 and the sleeve160 are preferably constructed of a tough plastic having good moldingqualities, high tensile strength in the order of 5,000 to 13,000 p.s.i(A.S.T.M., D 638, D 651), good flexural strength comparable to 8,000 to14,000 p.s.i. (A.S.T.M., D 790) and a Rockwell hardness of about 100 to120. Such plastics as nylon, polyvinyls, Teflon, polyethylene, ureaformaldehyde, methylmethacrylates, modified styrene, and polyacrylicsmay be used for purposes of forming these parts. Softer, more flexiblenon-rigid vinyl chloride polymers and copolymers, vinyl chloride-acetateresins, rubber, polyethylenes, and elastomeric types of plastics canalso be used.

One skilled in this art will know that various monomers and elastometercompositions can be formulated with or without fillers and plasticizersto produce molded parts having the desired physical and chemicalproperties to be suitable for use as the washer and sleeve parts andsame can be cut from extruded plastic hose having the desired inside andoutside diameters, or formed by compression or injection molding with orwithout machining to present a smooth bottom surface 182 and the properinternal dimensions and clearances, to maintain the spaces 124 and 126.

While the drawing discloses this invention in relation to a vegetablejuicing machine, it is to be understood that this invention applies toany centrifugal device having a driving means and a driven meanscarrying a working member at a high rotational speed and adapted to doWork upon a stationary workpiece or a material wherein conditions ofimbalance and vibration in the principle moving parts occur. The pins,96 and 132 maintain a positive driving action between the centrifugalhub 30 and the working member 46. Any means of attaching the hub withthe working members can be used which provides a direct driving actionbetween these members yet allows pivot 106 to function therebetween andalso allows easy assembly and disassembly.

The device shown in the drawing is in scale with an embodiment in whichthe mass weight of the hub is about 32 02., the macerator disc about 9oz. and the basket is about 22 oz. The relative movement permitted bythe pivot 106 is related to accommodate about a 1 oz. excess weightdeveloping at one point on the periphery of the basket of a diameter of7 inches. The speed of rotation in the order of 2,000 r.p.m. and higheris well above the oscillatory moment of the inertias involved at 7 inchdiameter and are further dampened by the radial friction and pivotalaction exerted by the parts. It is appreciated that with the weightsmentioned for the parts, the tilt angle of the rotating parts is only afew minutes or part of a degree. Although this is critical for dampeningundesirable vibration, the pivotal shift accomplished by the inventionand creation of the new center of rotation takes place progressively asneeded with little if any vibration building up at any time. As soon asan imbalance developes the device restores itself to balancedconditions.

It is apparent that other modifications of the structures shown can bemade without departing from this invention. Thus, the hub 30 may beconstructed integral with the collar 80, omitting the drive or shearpins 92, and the flange 88 can be a separable unit adapted to be atfixedto the integral flywheel by any suitable means after the balance plateis in position. The balance plate 100 can have a double flangearrangement with a top flange extending radially from the surface overthe surface 90. The collar 80 can be formed in two parts, eachencompassing one-half of the circumference of the hub. The ball 106 andsocket 112 arrangement can be reversed. The cap 54 can be replaced by aresilient flat washer encompassing the pivot shaft 108 and held in placeby a lock nut engaging the threaded portion 108. The shaft 34 and thehub 30 can be constructed as integral parts with the recess 74 servingas the socket joint.

Although but one specific embodiment of this invention has been hereinshown and described, it will be understood that details of theconstruction shown may be altered or omitted without departing from thespirit of the invention as defined by the following claims.

What is claimed is:

1. A centrifugal cutting device having a rotatable driving meanscarrying a Working means for high speed contact with a work piececomprising:

(a) means supporting said working means pivotally carried at the axis ofrotation by said driving means;

(b) means providing limited radial and circumferential movement betweensaid support means and said working means; and

(c) means for resiliently holding said working means axially against theperiphery of said support means whereby said working member and saidsupport means are adapted to move relative to said driving means underan imbalance of said working member.

2. A centrifugal cutting device in accordance with claim 1 in which:

(a) said driving means comprises a flywheel mounted on the end of arotatable drive shaft;

(b) said flywheel having a recess in its surface on the side oppositesaid shaft;

(0) said recess having a circumferential inwardly depending flange aboutits periphery; and

((1) said support means comprising a balance plate pivotally mounted atthe axis of rotation within said recess and contained therein by saidperipheral flange.

3. A centrifugal cutting device in accordance with claim 2 in which:

(a) said flywheel has a central recess opening to said balance plate;

(b) a pivot shaft is mounted through said balance plate with one endpivotally mounted within said recess;

(c) a drive pin extends from said flywheel into a blind bore hole insaid balance plate; and

(d) resilient washer means are provided between said drive pin and saidblind bore hole.

4. A centrifugal cutting device in accordance with claim 3 in which:

(a) said blind bore hole has a conical bottom engaging the peripheralcorner edge of said resilient washer means.

5. A centrifugal cutting device in accordance with claim 3 in which:

(a) said drive shaft extends into the recess of. said flywheel; and

(b) said pivot shaft engages said drive shaft in a ball and socketrelationship.

6. A centrifugal cutting device in accordance with claim in which:

(a) said drive shaft has a ball socket at the end thereof; and

(b) said pivot shaft has a ball joint adapted to pivotally engage saidsocket.

7. A centrifugal cutting device in accordance with claim 2 in which:

(a) said balance plate has a marginal edge extending circumferentiallytherefrom;

(b) said inwardly depending flange of said flywheel overlaps and axiallyengages the marginal edge "of said balance plate; and 1 (c) theperipheral surfaces of said balance plate are uniformly spaced from theinner axial surfaces of said recess in said flywheel.

8. A centrifugal cutting device in accordance with claim 7 in which:

(a) said flywheel has a detachable collar defining said recess and saidinwardly depending flange;

(b) said collar has a radial bore through a side wall thereof matching aradial bore in the body of said flywheel; and

(c) a shear pin engages said matching bores to hold said flywheel andcollar as a rotatable unit.

9. A centrifugal cutting device in accordance with claim 1 in which:

(a) said Working means includes a flat circular member with cuttingteeth on its peripheral surface and a catch basket therearound adaptedto receive a stationary work piece therein in engagement with saidcutting teeth;

(b) said balance plate has a raised peripheral edge engaging saidworking means radially of the axis of rotation thereof;

(c) a second drive pin extends from said balance plate into a bore holein said working means, said bore hole being circumferentially spacedfrom said second drive pin; and

(d) the means for resiliently holding said working means axially againstthe periphery of said support means comprises a cap member engaging saidshaft, a tubular friction member supported by said cap member and biasedagainst said working means.

10. In a high speed machine adapted to macerate juicecontaining fibrousmaterials and separate the juice and fibers thereof, wherein saidfibrous materials are introduced through a fixed inlet into a rotatingperforated basket subject to vibration due to uneven accumulations ofsaid fibrous material therein, the combination of:

(a) a flat base plate in said basket having a central bore;

(b) a cutter disc on said base plate with a central bore in alignmentwith the central bore of said base plate and having cutting teethextending upwardly along its periphery in close proximity to said fixedinlet;

(c) a rotatable shaft in said machine with a socket joint at theextended end thereof;

(d) a flywheel hub member aflixed to the end of said shaft;

(c) said hub member having a substantially cylindrical 10 outer wall,and a flat face on the side opposite said shaft with a central recess insaid face receiving said socket joint of said shaft;

(f) a collar member encompassing the outer wall of said hub and aflixedthereto by means of a shear member;

(g) said collar member having a peripheral shoulder engaging the outeredge of said flat face of said hub member and a peripheral inwardlydepending flange circumferentially spaced from said flat face;

(h) a balance plate having a central bore axially aligned with saidsocket joint on the end of said shaft;

(i) said balance plate having a flat bottom face and a radial flangeextending under said circumferential flange of said collar member;

(j) said balance plate having its peripheral surface spaced from theinner surfaces of said collar member;

(k) a pivot pin affixed within the central bore of said balance plate;

(1) said pivot pin having a ball joint at its bottom end in engagementwith the socket joint of said rotatable shaft and supporting saidbalance plate within said collar with its radial flange axially engagedby the inwardly depending flange of said collar member;

(m) the end of said pivot pin extending through the central bores ofsaid cutter disc and said base plate;

(n) a first drive pin extending from said hub member into a blind borein said balance plate radially spaced from said recess;

(0) a second drive pin extending from said balance plate into a pair ofaligned radially spaced bores in said cutter disc and said base plate,said second drive pin having a diameter less than the diameters of saidbores to provide lateral spacing therein;

(p) a detachable cap member aflixed to the extended end of said pivotpin having its base spaced from the top of said cutter disc; and

(q) a peripheral resilient sleeve in said cap member with means biasingsaid sleeve into contact with cutter disc whereby said base plate andcutter disc are adapted to tilt about said pivot axis on the sideopposite the accumulation of an imbalance in said basket about the whirlaxis of said machine an amount sufficient to increase the proximity ofsaid cutting teeth to said fixed inlet to increase the cutting ratethereof on said opposite side and centrifuge said increased cuttings tothe radially adjacent portion of the basket and automatically compensatefor said imbalance.

References Cited UNITED STATES PATENTS 2,466,153 4/ 1949 Chamberlin210-367 X 2,519,813 8/1950 Bayless 210365 3,165,132 1/1965 Moline 414676 3,407,858 10/ 1968 Smith et al. 146-76 W. GRAYDON ABERCROMBIE,Primary Examiner US. Cl. X.R. 146-3

